KR830000932B1 - Block bearing carded joint - Google Patents

Abstract

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Description

Block bearing carded joint

1 and 2 are front and side views, respectively, of a conventional cardan joint of the outer centering block bearing type.

3 is a perspective view of a flange of a cardan joint of the present invention.

5 is a perspective view of a block bearing of the present invention engaged with the flange shown in FIG.

5, 6 and 7 are a plan view, a back view and a side view of a conventional block bearing, respectively.

8, 9 and 10 are plan, rear and side views, respectively, of a block bearing of the present invention having a cylindrical centering bearing surface.

11 is a side view of a block bearing of the present invention having a conical centering bearing surface.

12 is a side view of a transmission with cardan joints installed at its ends.

13 is a side view of another type of transmission.

14 is a partial cross-sectional view of a cardan joint installed in a transmission.

The present invention relates to a block bearing cardan joint.

Conventional cardan joints used to join each end of two rotating shafts are pivotally mounted to the jaws via two jaws fixed to the two shafts respectively and two pairs of trunnions coaxially arranged. And a spider which acts to transmit rotational torque between the jaws. In this type of cardan joint, the two pairs of trunnions are able to reciprocate in two bearings respectively installed in the jaws.

In the case of a rigid joint, the bearing is machined into the jaw's arm to be formed as part of the jaw.

On the other hand, in a block bearing type joint having a somewhat complex structure as described in French Patent 756,038, the jaw is composed of three parts. In such a joint, each jaw consists of a flange fixed to one of the shafts to be joined to each other, and two bearings such as a needle bearing, the bearing comprising a block fixed to the flange by a screw, A centering bearing surface is provided which is formed by a tenon which protrudes on the surface and is keyed to the flange to act to deliver torque to the flange, and a portion of the cylindrical surface which is generally located at the outer periphery of the bearing.

The centering means, which consist of a sheet formed in each bearing and an end member projecting on the support surface of the flange, cooperate with each other so that each bearing can be accurately positioned in position radially.

That is, the end member is formed with a bore having a diameter corresponding to the diameter of the centering bearing surface, and the centering bearing surface is accommodated therein, thereby accurately centering the block bearing while keeping it exactly in the radial direction.

The relationship between the centering of the block bearing and the width of the tenon acting to transmit the torque, as the centering extends from the outside of the block bearing in such a way that it accommodates the circumference of the block bearing and holds the block bearing exactly in place in the radial direction. Due to this, the space occupied by the joint increases, and due to the relationship between the breaking strength of the axial size of the block bearing, the support surface of the block provided around the fixing hole is not distributed sufficiently with respect to the flange, so that the block bearing It tends to be inclined and also provides the centering end member on the flange, which prevents machining of the flange's support surface by broaching and machining only by turning. As the smoothness becomes worse, it causes a slight sphericalization. The blocks do not position correctly, and is there are disadvantages that it is premature wear occurs as a result.

It is also known to hold the block bearing in place radially relative to the flange by projecting a shoulder on the support surface provided on the block of the block bearing, as described in French patents 690,313 and 866,450. In this case, a flat support surface is provided around the shoulder, which in turn does not provide accurate centering for the flange. In addition, it requires a fairly complex machining to provide the required smoothness to the surface.

Accordingly, it is an object of the present invention to ensure the centering of a block bearing by a flange while not causing the radial size of the joint to be larger than the radial size of the block bearing, thereby keeping the block bearing in place in the radial direction and accurately centering it, It removes the constraints on the degree of centering, the width of the tenin, the axial size of the block bearings and the breaking strength, and allows the support surfaces provided around the fixing holes to be sufficiently distributed with respect to the flanges and the smoothness of the surfaces in contact with each other. It is possible to eliminate the disadvantages of the conventional joints by increasing the and to provide a card joint which is easy to manufacture and low cost.

According to the present invention, a block bearing cardan joint for joining respective ends of two rotary shafts includes two flanges each fixed to the shaft, two pairs of block bearings each fixed to the flange by suitable fastening means, and torque Consists of a transmitting spider, the spider's trunnion is reciprocally mounted in the block bearing, and the block of the block bearing has a drive tenn engageable in a groove formed in the flange to center the block bearing to prevent it from being disengaged from the joint. The centering bearing surface is provided at least partially in contact with the centering bearing surface of the flange, the centering bearing surface being provided spaced from the spider center at a distance less than the distance from the center of the spider to the block fixing means at the base of the drive tenon. Consisting of the peripheral surface of the member It is rotatable with respect to the axis of the rotary shaft together with the centering bearing surface of the range, and the radial distance between the drive tenant and the shaft axis is larger than the radial distance between the centering bearing surface and the shaft axis.

According to the invention, the centering of the block bearing is brought about in proximity to the axis of the cardan joint, so that the centering is surely reached in the middle region of the block in which the tenon is placed, thereby making it possible to obtain a predetermined distance regardless of the width of the tenon. This can lead to centering, in addition to reducing the axial and radial size of the joints, as well as the need for projections on the support surface of the flanges at all, making machining of the support surface easier and better. Can be.

Hereinafter, with reference to the accompanying drawings will be described an embodiment of the present invention.

Conventional block bearing type joints 1 as shown in FIGS. 1 and 2 have two flanges 2, 3 oriented vertically to be mounted at each end of two shafts (not shown) coupled to each other (3). (Simplified illustration, the front flange 3 is not shown in FIG. 1) and a spider 4 having trunnions reciprocally mounted in a block bearing 5, such as a needle bearing. Include. The block bearing 5 is provided with a supporting block 6 having a fixing hole 7 into which a screw 8 to be coupled to the flange can be inserted.

Each block 6 of the block bearing 5 has an outer centering bearing surface 9 and a drive tenn insertable into a radial groove 11 formed in the support surface 12 of the flange to which the block bearing is to be fixed. Include. As the centering bearing surface 9 of the block 6 is surrounded and brought into contact with an end member 13 positioned around the support surface 12 of the flange, the block bearing is correctly positioned in relation to the axis. In addition, it is also prevented from being separated radially by the centrifugal force.

It should be noted that the end member 13 of each flange extends more radially than the two-stage bearings located opposite each other to protrude out of the support surface 12 of the flange.

In the joint of the present invention as shown in FIG. 3, the flange has a flat body for supporting the block bearing and a body 20 in which a bore 21 is formed for receiving a shaft end (not shown) to be joined. It consists of a flange 22 having a support surface. The support surface is composed of four support surfaces 24a, 24b, 25a, and 25b separated by grooves 26 and 27 respectively formed to receive the drive tenons of the block bearing. Fixing holes 23 are formed in each of the supporting surfaces so as to be spaced apart in the circumferential direction with respect to the flange axis.

The flange 22 is counterbore to form a hollow centering housing, which is formed at the intersection of the grooves 26, 27 with each other, ie closest to the axis of the joint. It consists of cylindrical portions 28, 29.

According to the present invention, two block bearings 30 and 31 having blocks 32 and 33 respectively as shown in FIG. 4 are provided for engagement with a flange as shown in FIG. Blocks 32 and 33 each have support surfaces 34a, 34b, 35a and 35b for contacting the support surfaces 24a, 24b, 25a and 25b of the flange, respectively. ) Is formed.

The support surfaces are separated by tenons 37 and 38 respectively received in the grooves 26 and 27 of the flange to transmit the rotating torque, and the flanges of the flange can be inserted into Fixing holes 36 corresponding to the fixing holes 23 are formed, respectively. End blocks 39 and 40 are formed at each of the block bearings 30 and 31 at the bases of the tenons 37 and 38 positioned closest to the axis of the jointer. The cylindrical circumferential surfaces 39 and 40 constitute a centering bearing surface for contacting the cylindrical portions 28 and 29, respectively, of the counter bore of the flange shown in FIG. In addition, each block bearing is formed with bores 43 and 44 for accommodating the trunnion of the spider so as to achieve torque transmission between the flanges of the joint.

The centering bearing surfaces 41 and 42 of the block bearings 30 and 31 extend in the axial direction beyond the widths of the tenons 37 and 38 so that the centering at the base as well as on each side of the tenon is carried out. Guarantees.

Thereafter, a conventional bearing block as shown in FIGS. 5, 6 and 7 is compared with the bearing block of the present invention as shown in FIGS. 8, 9 and 10. The improvements and advantages according to the invention will be described in more detail.

As shown in FIG. 1 and FIG. 2, the groove 11 formed in the support surface of the flange is formed in such a manner as to open its rear end due to machining problems, so that the centering end member is formed by the groove 11. (13) loses continuity, thereby making it impossible to provide outer centering at all in areas where outer centering is most needed.

As a result, the width of the groove 11 must be limited to a predetermined maximum width t as shown in FIG. 5 in order to be able to provide sufficient centering while avoiding not providing such outer centering too much. In addition, the block bearing must be limited to its minimum thickness (e) so that it can have a sufficient breaking strength, especially on the block side with the smallest cross section.

Because of these two conditions, in the conventional block bearing as shown in FIG. 5, the maximum distance D from the axis of the block bearing to the support surface of the block becomes relatively larger than the diameter of the bore of the block bearing.

On the other hand, in the block bearing of the present invention, the centering bearing surface is performed because the centering and the radial positioning of the block bearing are made not only around its periphery but also inward from the base of the driving tenon (shown in FIG. 4). The continuity is not lost by the grooves formed in the support surface of the flange, and as a result, the width of the driving tenon is determined irrespective of the formation of the centering bearing surface, and therefore the centering size does not affect the centering at all. Do not.

As a result, it is possible to significantly increase the width T (shown in FIG. 8) of the tenon, so that the maximum from the axis of the block bearing to the support surface of the block while maintaining the minimum thickness e of the block bearing as described above. The torque (F _x × d), (F) generated in the bearing block of the present invention by the radial force (F _X ) and the transverse force (F _y ) transmitted by the trunnion so that the distance (d) can be reduced. _r × d) (shown in FIGS. 8 and 9) is less than the torques (F _x × D) and (F _r × D) (shown in FIGS. 5 and 7) generated in conventional block bearings. do. 6 and 9 are conventional block bearings each having blocks having fixing holes spaced at equal intervals L and positioned at the same distance l from the longitudinal central plane of the flange and having the same height, respectively. And a block bearing of the present invention, respectively, in the conventional block bearing, a bearing surface having an outer centering radius (R) is surrounded by an end member of a flange having a thickness (C), which is occupied by a rotary joint. The space has a radius of H = R + C.

On the other hand, in the block bearing of the present invention, the bearing surface has an inner centering radius r, so that it does not need to be surrounded by the end member as in the case of the conventional block bearing as described above. It has a radius R which is equal to the radius of the block bearing, ie, smaller than the conventional radius H. In order to achieve the same result as that of the present invention in the conventional block bearing, the thickness C of the end member of the flange must be present in the radial range of the block bearing, and therefore, as shown in FIG. The support surface shown by the oblique line S around the hole must be cut out by the arc S. As a result, the support area of the hole circumference is unevenly distributed and the block bearing tends to be inclined.

In addition, in the joint of the present invention, the end member need not be provided on the flange, and no projections need to be formed on the support surfaces 24a, 24b, 25a, and 25b of the flange. The face can be machined using broaching or surfacing rather than turning, thus avoiding the slight conical or spherical shape that degrades smoothness, such conical or No detachment, deformation, rapid deterioration, or premature wear of the block bearings caused by the spheronization is prevented.

The centering bearing surface of the block located at the base of the tenon can extend laterally larger than both sides of the tenon, providing more contact surface between the block and the flange.

The centering block bearing is formed into a cylindrical shape that is easy to machine, but may be formed into a conical shape as indicated by 45 in FIG.

12 and 13 show two embodiments of cardan transmissions with block bearings of the present invention.

The transmission shown in FIG. 12 consists of two transmission parts 51 and 52, each of which includes cardan joints 53 and 54, respectively. The connecting shaft of the transmission part 51 is configured as a hollow tubular shaft 55, and the connecting shaft of the transmission part 52 is composed of a non-hollow shaft 56, and the shaft 56 is in the shaft 55. And then slide against it. The torque is to be delivered by the groove 57, for example.

In the embodiment as shown in FIG. 12, the groove consists of a groove extending linearly in the longitudinal direction. In addition, in the above embodiment, the cardan joints 53 and 54 have the same structure, so only the cardan joint 54 will be described later. The cardan joint 54 includes a jaw 58 that is coupled to the shaft 56, the jaw 58 having a bore 59 formed therein so that the trunnion 60 of the spider 61 is received therein. To the bushing 64. Two different trunnions 62 are provided in the block bearing 63, which block bearing 63 can be mounted to an output flange, not shown by screws. The shaft 55 is incapable of axial movement and engages in the groove of the output flange to act to transmit torque.

By the groove 57 formed in the shaft 56, the sliding movement between the two transmission parts 51, 52 is made.

In this embodiment, the sliding range is determined according to the length of the groove 67 formed in the shaft 55. A coating such as plastic is coated on the groove 67 of the shaft 55 or the groove 57 of the shaft 55 so as to maintain a proper friction state. In addition, a sealing member 66 is provided to prevent dust from being caught in the groove 57.

One end of the shaft 55 having the groove 67 is provided with a sheet for mounting the tube 68.

The tube 68 is welded between the jaws of the cardan joint 53 and the grooves of the shaft 55, the length of which is determined to provide a cardan transmission of a predetermined length.

FIG. 13 shows another embodiment of a cardan transmission, in which the sliding range is defined by the shaft 56 rather than the groove 67 of the shaft 55. FIG. The configuration is the same as in the embodiment shown in FIG. The grooves formed in the tube are preferably covered. The shaft 56 also includes a tube 69 mounted to the jaw 58, which is provided with a sealing member 70. A tube 68 of variable length is provided to provide a desired length of transmission.

As shown in FIG. 14, the trunnion 62 of the spider 61 is inserted into the bushing 64 after the bearing member 71 is inserted into the bushing 64. The bushing 64 located in the bore of the block bearing is formed into a thin wall so that the thickness of the bottom 75 is thicker than the thickness of its inner wall 74 and is held in place by the circular club 72. do. The bearing member 71 also comes into contact with the trunnion 62 in the bushing 64.

The sealing ring 73 provides a seal between the bushing 64 and the spider 61. By providing a circular clip 72 with variable thickness to adjust the looseness, it is possible to accurately center the bushing 64 in place.

The circular clip 72 is located in the groove 76 formed in the bore of the block bearing 63 to have a thickness equal to or greater than the maximum thickness of the circular clip.

As such, the block bearing is easily mounted and the spider 61 is completely centered by the use of the circular clip 72.

By using a circular clip having a variable thickness, it is possible to compensate the tolerances in the manufacturing of the block bearing 63 very accurately, so that the centering is made precisely, so that the transmission can be balanced even when there are many tolerances. . In addition, since the bushing 64 is provided in the block bearing 63, the block bearing 63 can be prevented from being worn by the bearing member 71.

While the embodiments of the present invention have been described so far, the present invention is not limited to such embodiments, and various other preparations can be made within the scope of the present invention.

Claims (1)

Two flanges 22 mounted to the two rotary shafts, and two pairs of block bearings 30 and 31 fixed to the flanges 22 by suitable fastening means so as to engage respective ends of the two rotary shafts with each other. And a spider for transmitting torque, the trunnion of the spider being reciprocally mounted to the block bearings 30 and 31, and the blocks 32 and 33 of the block bearing formed on flanges (26). Driving tenons 37, 38, which can be coupled to (27), (27), and centering bearing surfaces (28, 29) of the flange (22), centering bearing surfaces (41), ( In block-bearing cardan joints in which block bearings 30 and 31 can be accurately centered by providing 42, the drive of the centering bearing surfaces 41 and 42 of blocks 32 and 33 is provided. Spar at the base of the tenon 37, 38 at a distance less than the distance from the center of the spider to the block fixing means 36; It is composed of the peripheral surface of the end member 39, 40 provided further away from the center and rotatable about the axis of the rotating shaft together with the centering bearing surfaces 28, 29 of the flange 22, And a radial distance (R) between the shaft axis and the shaft axis is larger than the radial distance (r) between the centering bearing surface of the block bearing and the shaft axis (R).

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